Turbomachine with alternatingly spaced turbine rotor blades

ABSTRACT

A turbomachine includes a spool and a turbine section including a turbine rear frame, a turbine, and a support member. The turbine includes a first plurality of turbine rotor blades and a second plurality of turbine rotor blades, the first plurality of turbine rotor blades and second plurality of turbine rotor blades alternatingly spaced along the axial direction and rotatable with one another. The support member extends between the first plurality of turbine rotor blades and the spool and couples the first plurality of turbine rotor blades to the spool. The turbomachine also includes a bearing assembly including a bearing, the bearing rotatably supporting the support member and supported by the turbine rear frame, the bearing spaced apart from the spool along the radial direction.

FIELD

The present subject matter relates generally to a turbomachine, and more particularly, to a turbine of a turbomachine having alternatingly spaced turbine rotor blades and a bearing assembly having a radially outer rear bearing.

BACKGROUND

Gas turbine engines generally include a turbine section downstream of a combustion section that is rotatable with a compressor section to rotate and operate the gas turbine engine to generate power, such as propulsive thrust. General gas turbine engine design criteria often include conflicting criteria that must be balanced or compromised, including increasing fuel efficiency, operational efficiency, and/or power output while maintaining or reducing weight, part count, and/or packaging (i.e. axial and/or radial dimensions of the engine).

Within at least certain gas turbine engines, the turbine section may include interdigitated rotors (i.e., successive rows or stages of rotating airfoils or blades). For example, a turbine section may include a turbine having a first plurality of low speed turbine rotor blades and a second plurality of high speed turbine rotor blades. The first plurality of low speed turbine rotor blades may be interdigitated with the second plurality of high speed turbine rotor blades. Such a configuration may result in a more efficient turbine.

However, several problems may arise with such a configuration relating to unwanted vibrations, clearance issues between the first and second pluralities of rotor blades, etc. Accordingly, an improved turbine with interdigitated turbine rotor blades would be useful.

BRIEF DESCRIPTION

Aspects and advantages of the invention will be set forth in part in the following description, or may be obvious from the description, or may be learned through practice of the invention.

In one exemplary embodiment of the present disclosure a turbomachine defining a radial direction and an axial direction is provided. The turbomachine includes a spool; and a turbine section including a turbine rear frame, a turbine, and a support member, the turbine including a first plurality of turbine rotor blades and a second plurality of turbine rotor blades, the first plurality of turbine rotor blades and second plurality of turbine rotor blades alternatingly spaced along the axial direction and rotatable with one another, the support member extending between the first plurality of turbine rotor blades and the spool and coupling the first plurality of turbine rotor blades to the spool. The turbomachine also includes a bearing assembly including a bearing, the bearing rotatably supporting the support member and supported by the turbine rear frame, the bearing spaced apart from the spool along the radial direction.

In certain exemplary embodiments the first plurality of turbine rotor blades is configured as a plurality of low-speed turbine rotor blades, and wherein the second plurality of turbine rotor blades is configured as a plurality of high-speed turbine rotor blades.

For example, in certain exemplary embodiments the bearing of the bearing assembly is a first bearing, wherein the support member is a low speed support member, wherein the turbine section further includes a high speed support member, and wherein the bearing assembly further includes a second bearing rotatably supporting the high-speed support member.

For example, in certain exemplary embodiments the turbine section further includes a turbine center frame and a frame support member, the frame support member coupled to the turbine center frame, wherein the second bearing is positioned between the high-speed support member and the frame support member.

For example, in certain exemplary embodiments the second bearing is axially aligned with the plurality of low-speed turbine rotor blades, the plurality of high-speed turbine rotor blades, or both.

For example, in certain exemplary embodiments the bearing assembly further includes a third bearing rotatably supporting the high-speed support member and positioned between the high-speed support member and the frame support member.

For example, in certain exemplary embodiments the plurality of low-speed turbine rotor blades each extend between a radially inner end and a radially outer end, and wherein at least two of the plurality of low-speed turbine rotor blades are spaced from one another along the axial direction and coupled to one another at the radially outer ends.

For example, in certain exemplary embodiments the plurality of high-speed turbine rotor blades each extend between a radially inner end and a radially outer end, and wherein at least two of the plurality of high-speed turbine rotor blades are spaced from one another along the axial direction and coupled to one another at the radially inner ends.

In certain exemplary embodiments the turbomachine may further include a gearbox, wherein the first plurality of turbine rotor blades is rotatable with the second plurality of turbine rotor blades through the gearbox.

For example, in certain exemplary embodiments the bearing of the bearing assembly is aligned with, or positioned aft of, the gearbox along the axial direction.

In certain exemplary embodiments the turbomachine defines a longitudinal centerline and a flowpath radius, the flowpath radius extending along the radial direction from the longitudinal centerline to a radially inner end of an aft-most turbine rotor blade of the first plurality of turbine rotor blades, wherein the bearing of the bearing assembly defines a bearing radius, the bearing radius extending along the radial direction from the longitudinal centerline to an inner-most attachment point of the bearing to the support member, wherein the bearing radius is equal to at least about ten percent of the flowpath radius.

For example, in certain exemplary embodiments the bearing radius is equal to at least about thirty percent of the flowpath radius.

In another exemplary embodiment of the present disclosure, a turbomachine defining a radial direction, an axial direction, and a longitudinal centerline is provided. The turbomachine includes a spool; and a turbine section including a turbine rear frame, a turbine, and a support member, the turbine including a first plurality of turbine rotor blades and a second plurality of turbine rotor blades, the first plurality of turbine rotor blades and second plurality of turbine rotor blades alternatingly spaced along the axial direction and rotatable with one another, the support member extending between the first plurality of turbine rotor blades and the spool and coupling the first plurality of turbine rotor blades to the spool. The turbomachine also includes a bearing assembly including a bearing, the bearing rotatably supporting the support member and supported by the turbine rear frame. The turbomachine further defines a flowpath radius, the flowpath radius extending along the radial direction from the longitudinal centerline to a radially inner end of an aft-most first turbine rotor blade of the first plurality of turbine rotor blades, wherein the bearing of the bearing assembly defines a bearing radius, the bearing radius extending along the radial direction from the longitudinal centerline to an inner-most attachment point of the bearing to the support member, wherein the bearing radius is equal to at least about ten percent of the flowpath radius.

In certain exemplary embodiments the bearing radius is equal to at least about thirty percent of the flowpath radius.

In certain exemplary embodiments the bearing is spaced apart from the spool along the radial direction.

In certain exemplary embodiments the first plurality of turbine rotor blades is configured as a plurality of low-speed turbine rotor blades, and wherein the second plurality of turbine rotor blades is configured as a plurality of high-speed turbine rotor blades.

For example, in certain exemplary embodiments the bearing of the bearing assembly is a first bearing, wherein the support member is a low speed support member, wherein the turbine section further includes a high speed support member, and wherein the bearing assembly further includes a second bearing rotatably supporting the high-speed support member.

For example, in certain exemplary embodiments the turbine section further includes a turbine center frame and a frame support member, the frame support member coupled to the turbine center frame, wherein the second bearing is positioned between the high-speed support member and the frame support member.

For example, in certain exemplary embodiments the second bearing is axially aligned with the plurality of low-speed turbine rotor blades, the plurality of high-speed turbine rotor blades, or both.

In certain exemplary embodiments the bearing of the bearing assembly is a first bearing, wherein the bearing assembly further includes a second bearing and a third bearing, wherein the support member is a first support member, wherein the turbine section further includes a second support member and a center frame support assembly, wherein the second and third bearings each support the second support member at a radially outer side and are supported by the center frame support assembly at a radially inner side.

These and other features, aspects and advantages of the present invention will become better understood with reference to the following description and appended claims. The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and, together with the description, serve to explain the principles of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

A full and enabling disclosure of the present invention, including the best mode thereof, directed to one of ordinary skill in the art, is set forth in the specification, which makes reference to the appended figures, in which:

FIG. 1 is a schematic cross sectional view of an exemplary gas turbine engine incorporating an exemplary embodiment of a turbine section according to an aspect of the present disclosure;

FIG. 2 is a close-up, schematic, cross sectional view of a turbine section in accordance with an exemplary aspect of the present disclosure; and

FIG. 3 is cross sectional view depicting exemplary blade pitch angles of a turbine of a turbine section in accordance with an exemplary embodiment of the present disclosure.

Repeat use of reference characters in the present specification and drawings is intended to represent the same or analogous features or elements of the present invention.

DETAILED DESCRIPTION

Reference will now be made in detail to present embodiments of the invention, one or more examples of which are illustrated in the accompanying drawings. The detailed description uses numerical and letter designations to refer to features in the drawings. Like or similar designations in the drawings and description have been used to refer to like or similar parts of the invention.

As used herein, the terms “first”, “second”, and “third” may be used interchangeably to distinguish one component from another and are not intended to signify location or importance of the individual components.

The terms “forward” and “aft” refer to relative positions within a gas turbine engine or vehicle, and refer to the normal operational attitude of the gas turbine engine or vehicle. For example, with regard to a gas turbine engine, forward refers to a position closer to an engine inlet and aft refers to a position closer to an engine nozzle or exhaust.

The terms “upstream” and “downstream” refer to the relative direction with respect to fluid flow in a fluid pathway. For example, “upstream” refers to the direction from which the fluid flows, and “downstream” refers to the direction to which the fluid flows.

The terms “coupled,” “fixed,” “attached to,” and the like refer to both direct coupling, fixing, or attaching, as well as indirect coupling, fixing, or attaching through one or more intermediate components or features, unless otherwise specified herein.

The singular forms “a”, “an”, and “the” include plural references unless the context clearly dictates otherwise.

The terms “low speed” and “high-speed” refer to relative speeds, such as relative rotational speeds, of two components during operations of the turbomachine, and do not imply or require any minimum or maximum absolute speeds.

Approximating language, as used herein throughout the specification and claims, is applied to modify any quantitative representation that could permissibly vary without resulting in a change in the basic function to which it is related. Accordingly, a value modified by a term or terms, such as “about”, “approximately”, and “substantially”, are not to be limited to the precise value specified. In at least some instances, the approximating language may correspond to the precision of an instrument for measuring the value, or the precision of the methods or machines for constructing or manufacturing the components and/or systems. For example, the approximating language may refer to being within a 10 percent margin.

Here and throughout the specification and claims, range limitations are combined and interchanged, such ranges are identified and include all the sub-ranges contained therein unless context or language indicates otherwise. For example, all ranges disclosed herein are inclusive of the endpoints, and the endpoints are independently combinable with each other.

The present disclosure is generally related to a turbomachine including a turbine section having a turbine with a plurality of alternatingly spaced turbine rotor blades. More specifically, the turbine includes a first plurality of turbine rotor blades alternatingly spaced with, and rotatable with (which, as used herein, refers to two components being rotatable relative to one another), a second plurality of turbine rotor blades. For the present disclosure, the turbomachine further includes a spool and a support member, the support member extending between the first plurality of turbine rotor blades and the spool and coupling the first plurality of turbine rotor blades to the spool. Further the turbomachine includes a bearing assembly having a bearing. The bearing rotatably supports the support member and is supported by a turbine rear frame within the turbine section. The bearing is spaced apart from the spool along the radial direction. Additionally, in certain exemplary embodiments, the bearing may be aligned with the turbine rear frame.

For example, in at least certain exemplary embodiments, the turbomachine further defines a flowpath radius, the flowpath radius extending along a radial direction from a longitudinal centerline of the turbomachine to a radially inner end of a first turbine rotor blade of the first plurality of turbine rotor blades. The bearing of the bearing assembly may similarly define a bearing radius, the bearing radius extending along the radial direction from the longitudinal centerline to an inner-most attachment point of the bearing to the support member. The bearing radius may be equal to at least about ten percent of the flowpath radius.

Inclusion of a bearing in accordance with such exemplary embodiments may provide more robust support for the first plurality of turbine rotor blades where it may be most needed. Specifically, in certain configurations, it may be difficult to maintain clearances at a radially outer end of the aft most turbine rotor blade due to, e.g., a relatively large size of such turbine rotor blade. Positioning the bearing in the manner described herein may assist with maintaining these clearances, despite the difficulties that may arise with moving the bearing radially outward.

Referring now to the drawings, wherein identical numerals indicate the same elements throughout the figures, FIG. 1 is a schematic cross-sectional view of a gas turbine engine in accordance with an exemplary embodiment of the present disclosure. More particularly, for the embodiment of FIG. 1, the gas turbine engine is a high-bypass turbofan jet engine 10, referred to herein as “turbofan engine 10.” As shown in FIG. 1, the turbofan engine 10 defines an axial direction A (extending parallel to a longitudinal centerline 12 provided for reference), a radial direction R, and a circumferential direction (i.e., a direction extending about the axial direction A; not depicted). In general, the turbofan 10 includes a fan section 14 and a core turbine engine 16 disposed downstream from the fan section 14.

The exemplary core turbine engine 16 depicted generally includes a substantially tubular outer casing 18 that defines an annular inlet 20. The outer casing 18 encases, in serial flow relationship, a compressor section including a booster or low pressure (LP) compressor 22 and a high pressure (HP) compressor 24; a combustion section 26; a turbine section including a high pressure (HP) turbine 28 and a low pressure (LP) turbine 30; and a jet exhaust nozzle section 32. The compressor section, combustion section 26, and turbine section together define a core air flowpath 37 extending from the annular inlet 20 through the LP compressor 22, HP compressor 24, combustion section 26, HP turbine section 28, LP turbine section 30 and jet nozzle exhaust section 32. A high pressure (HP) shaft or spool 34 drivingly connects the HP turbine 28 to the HP compressor 24. A low pressure (LP) shaft or spool 36 drivingly connects the LP turbine 30 to the LP compressor 22.

For the embodiment depicted, the fan section 14 includes a variable pitch fan 38 having a plurality of fan blades 40 coupled to a disk 42 in a spaced apart manner. As depicted, the fan blades 40 extend outwardly from disk 42 generally along the radial direction R. Each fan blade 40 is rotatable relative to the disk 42 about a pitch axis P by virtue of the fan blades 40 being operatively coupled to a suitable actuation member 44 configured to collectively vary the pitch of the fan blades 40, e.g., in unison. The fan blades 40, disk 42, and actuation member 44 are together rotatable about the longitudinal axis 12 by LP shaft 36 across a power gear box 46. The power gear box 46 includes a plurality of gears for stepping down the rotational speed of the LP shaft 36 to a more efficient rotational fan speed.

Referring still to the exemplary embodiment of FIG. 1, the disk 42 is covered by rotatable spinner cone 48 aerodynamically contoured to promote an airflow through the plurality of fan blades 40. Additionally, the exemplary fan section 14 includes an annular fan casing or outer nacelle 50 that circumferentially surrounds the fan 38 and/or at least a portion of the core turbine engine 16. It should be appreciated that for the embodiment depicted, the nacelle 50 is supported relative to the core turbine engine 16 by a plurality of circumferentially-spaced outlet guide vanes 52. Moreover, a downstream section 54 of the nacelle 50 extends over an outer portion of the core turbine engine 16 so as to define a bypass airflow passage 56 therebetween.

During operation of the turbofan engine 10, a volume of air 58 enters the turbofan 10 through an associated inlet 60 of the nacelle 50 and/or fan section 14. As the volume of air 58 passes across the fan blades 40, a first portion of the air 58 as indicated by arrows 62 is directed or routed into the bypass airflow passage 56 and a second portion of the air 58 as indicated by arrow 64 is directed or routed into the LP compressor 22. The ratio between the first portion of air 62 and the second portion of air 64 is commonly known as a bypass ratio. The pressure of the second portion of air 64 is then increased as it is routed through the high pressure (HP) compressor 24 and into the combustion section 26, where it is mixed with fuel and burned to provide combustion gases 66.

The combustion gases 66 are routed through the HP turbine 28 where a portion of thermal and/or kinetic energy from the combustion gases 66 is extracted via sequential stages of HP turbine stator vanes 68 that are coupled to an inner casing (not shown) and HP turbine rotor blades 70 that are coupled to the HP shaft or spool 34, thus causing the HP shaft or spool 34 to rotate, thereby supporting operation of the HP compressor 24. The combustion gases 66 are then routed through the LP turbine 30 where a second portion of thermal and kinetic energy is extracted from the combustion gases 66 via sequential stages of a first plurality of LP turbine rotor blades 72 that are coupled to an outer drum 73, and a second plurality of LP turbine rotor blades 74 that are coupled to an inner drum 75. The first plurality of LP turbine rotor blades 72 and second plurality of LP turbine rotor blades 74 are alternatingly spaced and rotatable with one another through a gearbox (not shown) to together drive the LP shaft or spool 36, thus causing the LP shaft or spool 36 to rotate. Such thereby supports operation of the LP compressor 22 and/or rotation of the fan 38.

The combustion gases 66 are subsequently routed through the jet exhaust nozzle section 32 of the core turbine engine 16 to provide propulsive thrust. Simultaneously, the pressure of the first portion of air 62 is substantially increased as the first portion of air 62 is routed through the bypass airflow passage 56 before it is exhausted from a fan nozzle exhaust section 76 of the turbofan 10, also providing propulsive thrust. The HP turbine 28, the LP turbine 30, and the jet exhaust nozzle section 32 at least partially define a hot gas path 78 for routing the combustion gases 66 through the core turbine engine 16.

It should be appreciated, however, that the exemplary turbofan engine 10 depicted in FIG. 1 is by way of example only, and that in other exemplary embodiments, the turbofan engine 10 may have any other suitable configuration. For example, in other exemplary embodiments, the turbine fan engine 10 may instead be configured as any other suitable turbomachine including, e.g., any other suitable number of shafts or spools, and excluding, e.g., the power gearbox 46 and/or fan 38, etc. Accordingly, it will be appreciated that in other exemplary embodiments, the turbofan engine 10 may instead be configured as, e.g., a turbojet engine, a turboshaft engine, a turboprop engine, etc., and further may be configured as an aeroderivative gas turbine engine or industrial gas turbine engine.

Referring now to FIG. 2, a schematic, side, cross-sectional view is provided of a turbine section 100 of a turbomachine in accordance with an exemplary embodiment of the present disclosure. The exemplary turbine section 100 depicted in FIG. 2 may be incorporated into, e.g., the exemplary turbofan engine 10 described above with reference to FIG. 1. However, in other exemplary embodiments, the turbine section 100 may be integrated into any other suitable machine utilizing a turbine.

Accordingly, it will be appreciated that the turbomachine generally defines a radial direction R, an axial direction A, and a longitudinal centerline 102. Further, the turbine section 100 includes a turbine 104, with the turbine 104 of the turbine section 100 being rotatable about the axial direction A (i.e., includes one or more components rotatable about the axial direction A). For example, in certain embodiments, the turbine 104 may be a low pressure turbine (such as the exemplary low pressure turbine 30 of FIG. 1), or alternatively may be any other turbine (such as, a high pressure turbine, an intermediate turbine, a dual use turbine functioning as part of a high pressure turbine and/or a low pressure turbine, etc.).

Moreover, for the exemplary embodiment depicted, the turbine 104 includes a plurality of turbine rotor blades spaced along the axial direction A. More specifically, for the exemplary embodiment depicted, the turbine 104 includes a first plurality of turbine rotor blades 106 and a second plurality of turbine rotor blades 108. As will be discussed in greater detail below, the first plurality of turbine rotor blades 106 and second plurality of turbine rotor blades 108 are alternatingly spaced along the axial direction A.

Referring first to the first plurality of turbine rotor blades 106, each of the first plurality of turbine rotor blades 106 extends generally along the radial direction R between a radially inner end 110 and a radially outer end 112. Additionally, the first plurality of turbine rotor blades 106 includes a first turbine rotor blade 106A, a second turbine rotor blade 106B, and a third turbine rotor blade 106C, each spaced apart from one another generally along the axial direction A. At least two of the first plurality of turbine rotor blades 106 are spaced from one another along the axial direction A and coupled to one another at the respective radially outer ends 112. More specifically, for the embodiment depicted, each of the first turbine rotor blade 106A, the second turbine rotor blade 106B, and the third turbine rotor blade 106C are mechanically coupled to one another through their respective radially outer ends 112. More specifically, still, each of the first turbine rotor blade 106A, the second turbine rotor blade 106B, and the third turbine rotor blade 106C of the first plurality of turbine rotor blades 106 are coupled at their respective radially outer ends 112 through an outer drum 114.

Further, the second plurality of turbine rotor blades 108, each also extend generally along the radial direction R between a radially inner end 118 and a radially outer end 120. Additionally, for the embodiment depicted, the second plurality of turbine rotor blades 108 includes a first turbine rotor blade 108A, a second turbine rotor blade 108B, and a third turbine rotor blade 108C, each spaced apart from another generally along the axial direction A. For the embodiment depicted, at least two of the second plurality of turbine rotor blades 108 are spaced from one another along the axial direction A and coupled to one another at the respective radially inner ends 118. More specifically, for the embodiment depicted, each of the first turbine rotor blade 108A, the second turbine rotor blade 108B, and the third turbine rotor blade 108C of the second plurality of turbine rotor blades 108 are mechanically coupled to one another through their respective radially inner ends 118. More specifically, still, each of the first turbine rotor blade 108A, the second turbine rotor blade 108B, and the third turbine rotor blade 108C of the second plurality of turbine rotor blades 108 are coupled at their respective radially inner ends 118 through an inner drum 116.

It should be appreciated, however, that in other exemplary embodiments, the first plurality of turbine rotor blades 106 and/or the second plurality of turbine rotor blades 108 may be coupled together in any other suitable manner, and that as used herein, “coupled at the radially inner ends” and “coupled at the radially outer ends” refers generally to any direct or indirect coupling means or mechanism to connect the respective components. For example, in certain exemplary embodiments, the second plurality of turbine rotor blades 108 may include multiple stages of rotors (not shown) spaced along the axial direction A, with the first turbine rotor blade 108A, the second turbine rotor blade 108B, and the third turbine rotor blade 108C coupled to the respective stages of rotors at the respectively radially inner ends 118 through, e.g. dovetail base portions. The respective stages of rotors may, in turn, be coupled together to therefore “couple the second plurality of turbine rotor blades 108 at their respective radially inner ends 118.”

Referring still to the embodiment depicted in FIG. 2, as stated, the first plurality of turbine rotor blades 106 and the second plurality of turbine rotor blades 108 are alternatingly spaced along the axial direction A. As used herein, the term “alternatingly spaced along the axial direction A” refers to the second plurality of turbine rotor blades 108 including at least one turbine rotor blade positioned along the axial direction A between two axially spaced turbine rotor blades of the first plurality of turbine rotor blades 106. For example, for the embodiment depicted, alternatingly spaced along the axial direction A refers to the second plurality of turbine rotor blades 108 including at least one turbine rotor blade positioned between the first and second turbine rotor blades 106A, 106B of the first plurality of turbine rotor blades 106 along the axial direction A, or between the second and third turbine rotor blades 106B, 106C of the first plurality of turbine rotor blades 106 along the axial direction A. More specifically, for the embodiment depicted, the first turbine rotor blade 106A of the first plurality of turbine rotor blades 106 is positioned aft of the first turbine rotor blade 108A of the second plurality of turbine rotor blades 108; the second turbine rotor blade 106B of the first plurality of turbine rotor blades 106 is positioned between the first and second turbine rotor blades 108A, 108B of the second plurality of turbine rotor blades 108; and the third turbine rotor blade 106C of the first plurality of turbine rotor blades 106 is positioned between the second and third turbine rotor blades 108B, 108C of the second plurality of turbine rotor blades 108.

Notably, however, in other exemplary embodiments, the first plurality of turbine rotor blades 106 may have any other suitable configuration and/or the second plurality of turbine rotor blades 108 may have any other suitable configuration. For example, it will be appreciated that for the embodiments described herein, the first turbine rotor blade 106A, second turbine rotor blade 106B, and third turbine rotor blade 106C of the first plurality of turbine rotor blades 106 generally represent a first stage of turbine rotor blades, a second stage of turbine rotor blades, and a third stage of turbine rotor blades, respectively. It will similarly be appreciated that the first turbine rotor blade 108A, second turbine rotor blade 108B, and third turbine rotor blade 108C of the second plurality of turbine rotor blades 108 each also generally represent a first stage of turbine rotor blades, a second stage of turbine rotor blades, and a third stage of turbine rotor blades, respectively. Notably, it will be appreciated that the terms “first,” “second,” and “third” are used herein simply to distinguish components and that in other embodiments the components may have any other suitable name (e.g., in other embodiments, the third stage of turbine rotor blades represented by blade 108C, may be referred to as the “first stage” of turbine rotor blades of the turbine 104, the third stage of turbine rotor blades represented by blade 106C may be referred to as the “second stage” of turbine rotor blades of the turbine 104, etc.). In other exemplary embodiments, the first plurality of turbine rotor blades 106 and/or the second plurality of turbine rotor blades 108 may include any other suitable number of stages of turbine rotor blades, such as two stages, four stages, etc., and further that in certain exemplary embodiments, the turbine 104 may additionally include one or more stages of stator vanes.

Referring still to the embodiment of FIG. 2, the turbine 104 further defines a midpoint 176 along the axial direction A. As used herein, the term “midpoint” refers generally to an axial location halfway between a forward-most forward edge of a forward-most turbine rotor blade of the turbine 104 and an aft-most aft edge of an aft-most turbine rotor blade of the turbine 104. Accordingly, for the embodiment depicted, the midpoint 176 of the turbine 104 is an axial location halfway between a forward-most forward edge 172 of the third turbine rotor blade 108C of the second plurality of turbine rotor blades 108 and an aft-most aft edge 174 of the first turbine rotor blade 106A of the first plurality of turbine rotor blades 106.

Moreover, for the embodiment depicted, the turbomachine further includes a gearbox 122 and a spool 124, with the first plurality of turbine rotor blades 106 and the second plurality of turbine rotor blades 108 rotatable with one another through the gearbox 122. In at least certain exemplary embodiments, the spool 124 may be configured as, e.g., the exemplary low pressure spool 36 described above with reference to FIG. 1. Additionally, the exemplary turbine section further includes a turbine center frame 150 and a turbine rear frame 152. The gearbox 122 is aligned with, or positioned aft of, the midpoint 176 of the turbine 104, and more particularly, for the embodiment depicted, is further aligned with the first turbine rotor blades 106A of the first plurality of turbine rotor blades 106 and the turbine rear frame 152. Notably, as used herein, the term “aligned with,” with reference to the axial direction A, refers to the two components and/or positions having at least a portion of the same axial position.

It should be appreciated, however, that in other exemplary embodiments, the spool 124 may be any other spool (e.g., a high pressure spool, an intermediate spool, etc.), and further that the gearbox 122 may be any other suitable speed change device positioned at any other suitable location. For example, in other exemplary embodiments, the gearbox 122 may instead be a hydraulic torque converter, an electric machine, a transmission, etc., and may be positioned forward of the midpoint 176 of the turbine 104.

Referring still to FIG. 2, the turbine section 100 includes a first support member assembly 126 having a first support member 128, and a second support member assembly 132 having a second support member 134. The first support member 128 extends between the first plurality of turbine rotor blades 106 and the spool 124. More specifically, the first support member 128 couples the radially inner end 110 of the first turbine rotor blade 106A of the first plurality of turbine rotor blades 106 to the spool 124, and further couples the first plurality of turbine rotor blades 106 to the gearbox 122. Additionally, the second support member 134 similarly couples the second plurality of turbine rotor blades 108, or rather the radially inner end 118 of the second turbine rotor blade 108B of the second plurality of turbine rotor blades 108, to the gearbox 122. Notably, however, in other exemplary embodiments, the first support member 128 may couple to any of the other turbine rotor blades within the first plurality of turbine rotor blades 106 at a radially inner end 110 (either directly or through, e.g., a rotor—not shown), and similarly, the second support member 134 may couple to any of the other turbine rotor blades of the second plurality of turbine rotor blades 108 at the radially inner ends 118 (either directly or through, e.g., a rotor—not shown).

Further, for the embodiment depicted the first support member assembly 126 includes a first flexible connection 138 attached to the first support member 128 at a juncture 140 of the first support member 128 (although, in other embodiments, the first flexible connection 138 may be formed integrally with the first support member 128). Similarly, the second support member assembly includes a second flexible connection 142 attached to, or formed integrally with, the second support member 134. The first flexible connection 138 and second flexible connection 142 allow for a flexible connection between the gearbox 122 and the first support number 128 and second support member 134, respectively. More particularly, the first flexible connection 138 and the second flexible connection 142 allow for a flexible connection between the gearbox 122 and the first plurality of turbine rotor blades 106 and the second plurality of turbine rotor blades 108, respectively. In certain embodiments, the first flexible connection 138, the second flexible connection 142, or both, may be configured as members having billows, splined connections with resilient material, etc.

The exemplary gearbox 122 depicted generally includes a first gear coupled to the first plurality of turbine rotor blades 106, a second gear coupled to the second plurality of turbine rotor blades 108, and a third gear coupled to the turbine center frame 150. More specifically, for the embodiment depicted, the gearbox 122 is configured as a planetary gear box. Accordingly, the first gear is a ring gear 144, the second gear is a sun gear 148, and the third gear is a planet gear 146 (or rather a plurality of planet gears 146 coupled to a planet gear carrier, not shown). More specifically, the exemplary turbine section 100 depicted further a center frame support assembly 154 coupled to the turbine center frame 150. The center frame support assembly 154, for the embodiment depicted, includes a first center frame support member 158 and a second center frame support member 160. The plurality of planet gears 146 (or the planet gear carrier, not shown) are fixedly coupled (i.e., fixed along a circumferential direction) to the turbine center frame 150 through the center frame support assembly 154, and more particularly, through the second center frame support member 160 of the center frame support assembly 154.

In such a manner, it will be appreciated that for the embodiment depicted the first plurality of turbine rotor blades 106 are configured to rotate in an opposite direction than the second plurality of turbine rotor blades 108. For example, the first plurality of turbine rotor blades 106 may be configured to rotate in a first circumferential direction C1 (see FIG. 3, below), while the second plurality of turbine rotor blades 108 may be configured to rotate in a second circumferential direction C2 (see FIG. 3, below), opposite the first circumferential direction C1. It should be understood, however, that although the structures provided herein therefore enable the turbine 104 to “counter-rotate,” in other embodiments, the turbine 104 may instead be configured to “co-rotate,” wherein the first plurality of turbine rotor blades 106 and the second plurality of turbine rotor blades 108 each rotate the same circumferential direction.

It should further be understood that the first circumferential direction C1 and the second circumferential direction C2 as used and described herein are intended to denote directions relative to one another. Therefore, the first circumferential direction C1 may refer to a clockwise rotation (viewed from downstream looking upstream) and the second circumferential direction C2 may refer to a counter-clockwise rotation (viewed from downstream looking upstream). Alternatively, the first circumferential direction C1 may refer to a counter-clockwise rotation (viewed from downstream looking upstream) and the second circumferential direction C2 may refer to a clockwise rotation (viewed from downstream looking upstream).

It will further be appreciated that for the embodiment depicted, the first plurality of turbine rotor blades 106 is configured as a plurality of low-speed turbine rotor blades, while the second plurality of turbine rotor blades 108 is configured as a plurality of high-speed turbine rotor blades. Such may be due to the gearing of the gearbox 122 and the fact that the first plurality of turbine rotor blades 106 are directly rotatable with the spool 124 (which may limit a rotational speed of the first plurality of turbine rotor blades 106). Regardless, it will be appreciated that in such an exemplary embodiment, the first support member assembly 126 is a low-speed support member assembly, and further, the second support member assembly 132 is a high-speed support member assembly.

Additionally, as previously discussed and as is depicted, the first plurality of turbine rotor blades 106 is coupled to the first gear, i.e., the ring gear 144, of the gearbox 122 through the first support member 128 of the first support member assembly 126, and further the first plurality of turbine rotor blades 106 is coupled to the spool 124 through the first support member 128 of the first support member assembly 126. More specifically, for the embodiment depicted the first support member 128 of the first support member assembly 126 extends from the radially inner end 110 of the first turbine rotor blade 106A of the first plurality of turbine rotor blades 106 to the spool 124. Notably, for the embodiment depicted, the first support member 128 is generally formed of a single, continuous member. However, in other exemplary embodiments, the first support member 128 may instead be a plurality of components joined in any suitable manner.

Moreover, as is depicted in the embodiment of FIG. 2, the second plurality of turbine rotor blades 108 is supported by the second support member 134 of the second support member assembly 132. Specifically, for the embodiment depicted, the second support member 134 is connected to the radially inner end 118 of the second turbine rotor blade 108B of the second plurality of turbine rotor blades 108. However, in other embodiments, the second support member 134 may be connected to the second plurality of turbine rotor blades 108 in any other suitable manner and at any other suitable location.

Further, still, the turbomachine depicted in FIG. 2 includes a bearing assembly 162. The bearing assembly 162 includes a bearing, and more specifically a first bearing 164, with the first bearing 164 rotatably supporting the first support member 128 of the first support member assembly 126 and being supported by the turbine rear frame 152. Specifically, for the embodiment depicted, the first bearing 164 is positioned between a rear frame support assembly 156 and the first support member 128 of the first support member assembly 126.

Referring still to FIG. 2, the first bearing 164 is spaced apart from the spool 124 along the radial direction R, and more particularly is located radially outward from the spool 124. More particularly, for the embodiment depicted, the turbomachine defines a flowpath radius 208 extending along the radial direction R from the longitudinal centerline 102 to the radially inner end 110 of an aft-most turbine rotor blade of the turbine 104 (i.e., the first turbine rotor blade 106A of the first plurality of turbine rotor blades 106). More specifically, for the purposes of defining the flowpath radius 208, the flowpath radius 208 extends from the longitudinal centerline 102 to the radially inner-most portion of the aft-most turbine rotor blade, and more specifically, still, to a radially inner-most portion of an airfoil portion of the aft-most turbine rotor blade of the first plurality of turbine rotor blades 106 (excluding any base, such as a dovetail-shaped base, which may be attached to a rotor, neither shown). Additionally, the first bearing 164 of the bearing assembly 162 defines a bearing radius 210 extending along the radial direction R from an innermost (i.e., radially innermost) attachment point of the first bearing 164 to the first support member 128 of the first support member assembly 126 to the longitudinal centerline 102. For the embodiment depicted, the bearing radius 210 is equal to at least about ten percent of the flowpath radius 208. For example, in certain exemplary embodiments, the bearing radius 210 may be at least about twenty percent of the flowpath radius 208, such as at least about thirty percent of the flowpath radius 208 such as at least about fifty percent of the flowpath radius 208, such as at least about seventy-five percent of the flowpath radius 208 (such as in the embodiment depicted), and up to about ninety-nine percent of the flowpath radius 208.

It will further be appreciated that for the embodiment depicted, the first bearing 164 of the bearing assembly 162 is aligned with, or positioned aft of the gearbox 122 along the axial direction A. Specifically, for the embodiment depicted, the first bearing 164 is positioned aft of the gearbox 122, and aligned with, or radially inward of, the turbine rear frame 152 of the turbomachine along the axial direction A.

Inclusion of a first bearing being located radially outward from a spool in the manner described herein may provide for a more stable turbine, despite the increased speeds at least certain portions of the first bearing will be required to tolerate. Additionally, inclusion of a bearing in accordance with such exemplary embodiments may provide more robust support for the first plurality of turbine rotor blades where it may be most needed. Specifically, in certain configurations, it may be difficult to maintain clearances at a radially outer end of an aft most turbine rotor blade due to, e.g., a relatively large size of such turbine rotor blade. Positioning a bearing in the manner described herein may assist with maintaining these clearances, despite the difficulties that may arise with moving the bearing radially outward.

Referring still to FIG. 2, the bearing assembly 162 further includes a second bearing 166 rotatably supporting the second support member 134 of the second support member assembly 132 (i.e., the high-speed support member for the embodiment depicted). More particularly, the bearing assembly 162 further includes a third bearing 168 also rotatably supporting the second support member 134 of the second support member assembly 132. The second bearing 166 and the third bearing 168 are each positioned between the second support member 134 of the second support member assembly 132 and the center frame support assembly 154, such that they are each supported by the turbine center frame 150. More specifically, for the embodiment depicted, the second bearing 166 and the third bearing 168 each support the second support member 134 of the second support member assembly 132 at a radially outer side and are supported by the center frame support assembly 154 at a radially inner side.

Notably, for the embodiment depicted, the second bearing 166 and the third bearing 168 are each axially aligned with the first plurality of turbine rotor blades 106, the second plurality of turbine rotor blades 108, or both. More specifically, the second bearing 166 and the third bearing 168 are each positioned aft of a forward edge 172 of the forward-most turbine rotor blade of the first plurality of turbine rotor blades 106 and second plurality of turbine rotor blades 108 and positioned forward of an aft edge 174 of the aft-most turbine rotor blade of the first plurality of turbine rotor blades 106 and second plurality of turbine rotor blades 108. More specifically, still, for the embodiment depicted, the second bearing 166 is positioned forward of the midpoint 176 of the turbine 104 and the third bearing 168 is positioned aft of the midpoint 176 of the turbine 104. With such a configuration, the second bearing 166 and the third bearing 168 may be oriented with a center of mass of the turbine 104 to more effectively rotatably support the turbine 104.

Furthermore, for the embodiment depicted, the bearing assembly 162 additionally includes a fourth bearing 170. The fourth bearing 170 of the bearing assembly 162 rotatably supports the spool 124. More particularly, for the exemplary turbomachine depicted the fourth bearing 170 is supported by the turbine center frame 150 through the center frame support assembly 154 (and more particularly, through the first center frame support member 158 of the center frame support assembly 154).

As is depicted schematically, for the embodiment depicted the second bearing 166 is configured as a ball bearing and the first bearing 164, third bearing 168, and fourth bearing 170 are each configured as a roller bearings. However, in other exemplary embodiments, the first bearing 164, second bearing 166, third bearing 168, and fourth bearing 170 may instead be configured in any other suitable manner, such as the other of a roller bearing or ball bearing, or alternatively, as a tapered roller bearing, an air bearing, etc.

It will further be appreciated that in at least certain exemplary embodiments, the first plurality of turbine rotor blades 106 and the second plurality of turbine rotor blades 108 may have any other suitable configuration. For example, in other exemplary embodiments, the first and/or second pluralities of turbine rotor blades 106, 108 may be configured in a split drum configuration. More specifically, in certain alternative exemplary embodiments, the first plurality of turbine rotor blades 106 may similarly include a first turbine rotor blade 106A, a second turbine rotor blade 106B, and a third turbine rotor blade 106C spaced along an axial direction A. A radially outer end 112 of the first turbine rotor blade 106A may be coupled to a radially outer end 112 of the second turbine rotor blade 106B, and a radially inner end 110 of the second turbine rotor blade 106B may be coupled to a radially inner end 110 of the third turbine rotor blade 106C. For example, the first turbine rotor blade 106A and second turbine rotor blade 106B of the first plurality of turbine rotor blades 106 may be coupled through a first outer drum, and further the second turbine rotor blade 106B and the third turbine rotor blade 106C of the first plurality of turbine rotor blades 106 may be coupled through a first inner drum.

Further, in certain of these alternative exemplary embodiments, the second plurality of turbine rotor blades 108 may similarly include a first turbine rotor blade 108A, a second turbine rotor blade 108B, and a third turbine rotor blade 108C spaced along an axial direction A, and more particularly, alternatingly spaced along the axial direction A with the first plurality of turbine rotor blades 106. A radially inner end 118 of the first turbine rotor blade 108A may be coupled to a radially inner end 118 of the third turbine rotor blade 108C, and further, a radially outer end 120 of the third turbine rotor blade 108C may be coupled to the radially outer end 120 of the second turbine rotor blade 108B. More specifically, the first turbine rotor blade 108A and third turbine rotor blade 108C may be coupled through a second inner drum 117, and the third turbine rotor blade 108C and the second turbine rotor blade 108B may be coupled through a second outer drum 115. Other configurations are contemplated as well.

Referring now to FIG. 3, an exemplary embodiment of an orientation of the first plurality of turbine rotor blades 106 and the second plurality of turbine rotor blades 108 is generally provided. The first plurality of turbine rotor blades 106 and the second plurality of turbine rotor blades 108 may be the same rotor blades discussed above with reference to, e.g., FIG. 2.

More specifically, the embodiment of FIG. 3 depicts a first stage of turbine rotor blades 106A of the first plurality of turbine rotor blades 106 and a first stage of turbine rotor blades 108A of the second plurality of turbine rotor blades 108. In at least certain exemplary embodiments, the first plurality of turbine rotor blades may be configured to rotate in a first circumferential direction C1, while the second plurality of turbine rotor blades may be configured to rotate in a second circumferential direction C2.

It will be appreciated that for the embodiment depicted, each of the turbine rotor blades 106A of the first plurality of turbine rotor blades 106 include an airfoil 180, and similarly, each of the turbine rotor blades 108A of the second plurality of turbine rotor blades 108 include an airfoil 182. The airfoils 180 each define an exit angle 184, and similarly the airfoils 182 each define an exit angle 186. The exit angles 184, 186 each represent an angular relationship of a longitudinal centerline 102 (i.e., of the turbomachine within which they are installed) to an exit direction of the gases flowing from an upstream end 188 towards a downstream end 190 of the respective airfoils 180, 182. For the embodiment depicted, the exit angle 184 may be a negative angle, such as a negative acute angle, while the exit angle 186 may be a positive angle, such as a positive acute angle (“positive” and “negative” being used herein to denote a relative value of the respective exit angles 184, 186 viewed from the same perspective). Notably, the exit angles 184, 186 of the airfoils 180, 182, respectively, a cause the first plurality of turbine rotor blades 106 and second plurality of turbine rotor blades 108 to rotate in the first and second circumferential directions C1, C2, respectively.

Referring still to FIG. 3, the airfoils 180, 182 may each further include a suction side 192 and a pressure side 194. The suction side 192 of the airfoils 180 are configured as convex toward the first circumferential direction C1 and the pressure side 194 of the airfoils 180 are configured as concave toward the first circumferential direction C1. The suction side 192 of the airfoils 182 are configured as convex toward the second circumferential direction C2 and the pressure side 194 of the airfoils 180 are configured as concave toward the second circumferential direction C2. Such a configuration may further result in the first plurality of turbine rotor blades 106 and second plurality of turbine rotor blades 108 rotating in the first and second circumferential directions C1, C2, respectively.

This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they include structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal languages of the claims. 

What is claimed is:
 1. A turbomachine defining a radial direction and an axial direction, the turbomachine comprising: a spool; a turbine section comprising a turbine rear frame, a turbine, and a support member, the turbine comprising a first plurality of turbine rotor blades and a second plurality of turbine rotor blades, the first plurality of turbine rotor blades and second plurality of turbine rotor blades alternatingly spaced along the axial direction and rotatable with one another, the support member extending between the first plurality of turbine rotor blades and the spool and coupling the first plurality of turbine rotor blades to the spool; and a bearing assembly comprising a bearing, the bearing rotatably supporting the support member and supported by the turbine rear frame, the bearing spaced apart from the spool along the radial direction.
 2. The turbomachine of claim 1, wherein the first plurality of turbine rotor blades is configured as a plurality of low-speed turbine rotor blades, and wherein the second plurality of turbine rotor blades is configured as a plurality of high-speed turbine rotor blades.
 3. The turbomachine of claim 2, wherein the bearing of the bearing assembly is a first bearing, wherein the support member is a low speed support member, wherein the turbine section further comprises a high speed support member, and wherein the bearing assembly further comprises a second bearing rotatably supporting the high-speed support member.
 4. The turbomachine of claim 3, wherein the turbine section further comprises a turbine center frame and a frame support member, the frame support member coupled to the turbine center frame, wherein the second bearing is positioned between the high-speed support member and the frame support member.
 5. The turbomachine of claim 3, wherein the second bearing is axially aligned with the plurality of low-speed turbine rotor blades, the plurality of high-speed turbine rotor blades, or both.
 6. The turbomachine of claim 4, wherein the bearing assembly further comprises a third bearing rotatably supporting the high-speed support member and positioned between the high-speed support member and the frame support member.
 7. The turbomachine of claim 2, wherein the plurality of low-speed turbine rotor blades each extend between a radially inner end and a radially outer end, and wherein at least two of the plurality of low-speed turbine rotor blades are spaced from one another along the axial direction and coupled to one another at the radially outer ends.
 8. The turbomachine of claim 2, wherein the plurality of high-speed turbine rotor blades each extend between a radially inner end and a radially outer end, and wherein at least two of the plurality of high-speed turbine rotor blades are spaced from one another along the axial direction and coupled to one another at the radially inner ends.
 9. The turbomachine of claim 1, further comprising: a gearbox, wherein the first plurality of turbine rotor blades is rotatable with the second plurality of turbine rotor blades through the gearbox.
 10. The turbomachine of claim 9, wherein the bearing of the bearing assembly is aligned with, or positioned aft of, the gearbox along the axial direction.
 11. The turbomachine of claim 1, wherein the turbomachine defines a longitudinal centerline and a flowpath radius, the flowpath radius extending along the radial direction from the longitudinal centerline to a radially inner end of an aft-most turbine rotor blade of the first plurality of turbine rotor blades, wherein the bearing of the bearing assembly defines a bearing radius, the bearing radius extending along the radial direction from the longitudinal centerline to an inner-most attachment point of the bearing to the support member, wherein the bearing radius is equal to at least about ten percent of the flowpath radius.
 12. The turbomachine of claim 11, wherein the bearing radius is equal to at least about thirty percent of the flowpath radius.
 13. A turbomachine defining a radial direction, an axial direction, and a longitudinal centerline, the turbomachine comprising: a spool; a turbine section comprising a turbine rear frame, a turbine, and a support member, the turbine comprising a first plurality of turbine rotor blades and a second plurality of turbine rotor blades, the first plurality of turbine rotor blades and second plurality of turbine rotor blades alternatingly spaced along the axial direction and rotatable with one another, the support member extending between the first plurality of turbine rotor blades and the spool and coupling the first plurality of turbine rotor blades to the spool; and a bearing assembly comprising a bearing, the bearing rotatably supporting the support member and supported by the turbine rear frame; wherein the turbomachine further defines a flowpath radius, the flowpath radius extending along the radial direction from the longitudinal centerline to a radially inner end of an aft-most first turbine rotor blade of the first plurality of turbine rotor blades, wherein the bearing of the bearing assembly defines a bearing radius, the bearing radius extending along the radial direction from the longitudinal centerline to an inner-most attachment point of the bearing to the support member, wherein the bearing radius is equal to at least about ten percent of the flowpath radius.
 14. The turbomachine of claim 13, wherein the bearing radius is equal to at least about thirty percent of the flowpath radius.
 15. The turbomachine of claim 13, wherein the bearing is spaced apart from the spool along the radial direction.
 16. The turbomachine of claim 13, wherein the first plurality of turbine rotor blades is configured as a plurality of low-speed turbine rotor blades, and wherein the second plurality of turbine rotor blades is configured as a plurality of high-speed turbine rotor blades.
 17. The turbomachine of claim 16, wherein the bearing of the bearing assembly is a first bearing, wherein the support member is a low speed support member, wherein the turbine section further comprises a high speed support member, and wherein the bearing assembly further comprises a second bearing rotatably supporting the high-speed support member.
 18. The turbomachine of claim 17, wherein the turbine section further comprises a turbine center frame and a frame support member, the frame support member coupled to the turbine center frame, wherein the second bearing is positioned between the high-speed support member and the frame support member.
 19. The turbomachine of claim 17, wherein the second bearing is axially aligned with the plurality of low-speed turbine rotor blades, the plurality of high-speed turbine rotor blades, or both.
 20. The turbomachine of claim 13, wherein the bearing of the bearing assembly is a first bearing, wherein the bearing assembly further comprises a second bearing and a third bearing, wherein the support member is a first support member, wherein the turbine section further comprises a second support member and a center frame support assembly, wherein the second and third bearings each support the second support member at a radially outer side and are supported by the center frame support assembly at a radially inner side. 